This document discusses various types of positive displacement rotary compressors. It describes the working principles of fixed vane, rolling piston compressors used in small refrigeration systems. It also explains multiple vane rotary compressors that have sliding vanes held against the cylinder by centrifugal force, producing multiple compression strokes per rotation. Additionally, it covers twin-screw and single-screw compressors that compress refrigerant as helical rotors mesh and unmesh, as well as scroll compressors that spiral refrigerant towards the discharge port. The key advantages and applications of each type are presented.

1. Lesson
20
Rotary, Positive
Displacement Type
Compressors
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2. The specific objectives of this lecture are to:
1. Discuss working principle and characteristics of a fixed vane, rolling piston
type compressor (Section 20.1)
2. Discuss working principle and characteristics of a multiple vane, rotary
compressor (Section 20.2, 20.3)
3. Discuss working principle and characteristics of a twin-screw type compressor
(Section 20.4.1)
4. Discuss working principle and characteristics of a single-screw type
compressor (Section 20.4.2)
5. Discuss working principle, characteristics and specific advantages of a scroll
compressor (Section 20.5)
At the end of the lecture, the student should be able to
1. Explain with schematics the working principles of rotary fixed and multiple
vane type compressors, single- and twin-screw type compressors and scroll
compressors.
2. Explain the performance characteristics, advantages and applications of
rotary, positive displacement type compressors.
20.1. Rolling piston (fixed vane) type compressors:
Rolling piston or fixed vane type compressors are used in small refrigeration
systems (upto 2 kW capacity) such as domestic refrigerators or air conditioners.
These compressors belong to the class of positive displacement type as
compression is achieved by reducing the volume of the refrigerant. In this type of
compressors, the rotating shaft of the roller has its axis of rotation that matches with
the centerline of the cylinder, however, it is eccentric with respect to the roller (Figure
20.1). This eccentricity of the shaft with respect to the roller creates suction and
compression of the refrigerant as shown in Fig.20.1. A single vane or blade is
positioned in the non-rotating cylindrical block. The rotating motion of the roller
causes a reciprocating motion of the single vane.
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3. Fixed vane
Cylinder block Roller
suction discharge
Discharge
valve
Fig.20.1: Working principle of a rolling piston type compressor
As shown in Fig.20.1, this type of compressor does not require a suction valve
but requires a discharge valve. The sealing between the high and low pressure sides
has to be provided:
- Along the line of contact between roller and cylinder block
- Along the line of contact between vane and roller, and
- between the roller and end-pates
The leakage is controlled through hydrodynamic sealing and matching between
the mating components. The effectiveness of the sealing depends on the clearance,
compressor speed, surface finish and oil viscosity. Close tolerances and good
surface finishing is required to minimize internal leakage.
Unlike in reciprocating compressors, the small clearance volume filled with
high-pressure refrigerant does not expand, but simply mixes with the suction
refrigerant in the suction space. As a result, the volumetric efficiency does not
reduce drastically with increasing pressure ratio, indicating small re-expansion
losses. The compressor runs smoothly and is relatively quiet as the refrigerant flow
is continuous.
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4. The mass flow rate of refrigerant through the compressor is given by:
L)BA(
60
N
4vv
V
m 22
e
V
e
SW
.
V
.
−⎟
⎠
⎞
⎜
⎝
⎛
⎟
⎠
⎞
⎜
⎝
⎛ π
⎟⎟
⎠
⎞
⎜⎜
⎝
⎛ η
=
⎟
⎟
⎟
⎠
⎞
⎜
⎜
⎜
⎝
⎛
η= (20.1)
where A = Inner diameter of the cylinder
B = Diameter of the roller
L = Length of the cylinder block
N = Rotation speed, RPM
ηV = Volumetric efficiency
ve = specific volume of refrigerant at suction
20.2. Multiple vane type compressors:
As shown in Fig.20.2, in multiple vane type compressor, the axis of rotation
coincides with the center of the roller (O), however, it is eccentric with respect to the
center of the cylinder (O’). The rotor consists of a number of slots with sliding vanes.
During the running of the compressor, the sliding vanes, which are normally made of
non-metallic materials, are held against the cylinder due to centrifugal forces. The
number of compression strokes produced in one revolution of the rotor is equal to
the number of sliding vanes, thus a 4-vane compressor produces 4 compression
strokes in one rotation.
In these compressors, sealing is required between the vanes and cylinder,
between the vanes and the slots on the rotor and between the rotor and the end
plate. However, since pressure difference across each slot is only a fraction of the
total pressure difference, the sealing is not as critical as in fixed vane type
compressor.
This type of compressor does not require suction or discharge valves,
however, as shown in Fig.20.3, check valves are used on discharge side to prevent
reverse rotation during off-time due to pressure difference. Since there are no
discharge valves, the compressed refrigerant is opened to the discharge port when it
has been compressed through a fixed volume ratio, depending upon the geometry.
This implies that these compressors have a fixed built-in volume ratio. The built-in
volume ratio is defined as “the ratio of a cell as it is closed off from the suction port to
its volume before it opens to the discharge port”. Since the volume ratio is fixed, the
pressure ratio, rp is given by:
k
b
s
d
p V
P
P
r =⎟⎟
⎠
⎞
⎜⎜
⎝
⎛
= (20.2)
where Pd and Ps are the discharge and suction pressures, Vb is the built-in volume
ratio and k is the index of compression.
Since no centrifugal force is present when the compressor is off, the multiple
vanes will not be pressed against the cylinder walls during the off-period. As a result,
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5. Fig.20.3: Sectional view of a multiple vane, rotary compressor
high pressure refrigerant from the discharge side can flow back into the side and
pressure equalization between high and low pressure sides take place. This is
beneficial from the compressor motor point-of-view as it reduces the required starting
torque. However, this introduces cycling loss due to the entry of high pressure and
hot refrigerant liquid into the evaporator. Hence, normally a non-return check valve is
used on the discharge side which prevents the entry of refrigerant liquid from high
pressure side into evaporator through the compressor during off-time, at the same
time there will be pressure equalization across the vanes of the compressor.
20.3. Characteristics of rotary, vane type compressors:
Rotary vane type compressors have low mass-to-displacement ratio, which in
combination with compact size makes them ideal for transport applications. The
Cylinder
block
Sliding
vanes
O’
O
SuctionDischarge
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Fig.20.2: Working principle of a multiple vane, rotary compressor

6. compressors are normally oil-flooded type, hence, oil separators are required. Both
single-stage (upto –40o
C evaporator temperature and 60o
C condensing temperature)
and two-stage (upto –50o
C evaporator temperature) compressors with the cooling
capacity in the range of 2 to 40 kW are available commercially. The cooling capacity
is normally controlled either by compressor speed regulation or suction gas throttling.
Currently, these compressors are available for a wide range of refrigerants such as
R 22, ammonia, R 404a etc.
20.4. Rotary, screw compressors:
The rotary screw compressors can be either twin-screw type or single-screw
type.
20.4.1. Twin-screw compressor:
The twin-screw type compressor consists of two mating helically grooved
rotors, one male and the other female. Generally the male rotor drives the female
rotor. The male rotor has lobes, while the female rotor has flutes or gullies. The
frequently used lobe-gully combinations are [4,6], [5,6] and [5,7]. Figure 20.4 shows
the [4,6] combination. For this [4,6] combination, when the male rotor rotates at 3600
RPM, the female rotor rotates at 2400 RPM.
As shown in Fig.20.5, the flow is mainly in the axial direction. Suction and
compression take place as the rotors unmesh and mesh. When one lobe-gully
combination begins to unmesh the opposite lobe-gully combination begins to mesh.
With 4 male lobes rotating at 3600 RPM, 4 interlobe volumes are per revolution, thus
giving 4 X 3600 = 14400 discharges per minute.
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Fig.20.5: Direction of refrigerant flow in a twin-screw compressor
Fig.20.4: Twin-screw compressor with 4 male lobes and 6 female gullies

8. Discharge takes place at a point decided by the designed built-in volume ratio, which
depends entirely on the location of the delivery port and geometry of the compressor.
Since the built-in volume ratio is fixed by the geometry, a particular compressor is
designed for a particular built-in pressure ratio. However, different built-in ratios can
be obtained by changing the position of the discharge port. The built-in pressure
ratio, rp given by:
k
b
s
d
p V
P
P
r =⎟⎟
⎠
⎞
⎜⎜
⎝
⎛
= (20.3)
Where Pd and Ps are the discharge and suction pressures, Vb is the built-in
volume ratio and k is the index of compression.
If the built-in pressure at the end of compression is less than the condensing
pressure, high pressure refrigerant from discharge manifold flows back into the
interlobe space when the discharge port is uncovered. This is called as under-
compression. On the other hand, if the built-in pressure at the end of compression is
higher than the condensing pressure, then the compressed refrigerant rushes out in
an unrestrained expansion as soon as the port is uncovered (over-compression).
Both under-compression and over-compression are undesirable as they lead to loss
in efficiency.
Lubrication and sealing between the rotors is obtained by injecting lubricating
oil between the rotors. The oil also helps in cooling the compressor, as a result very
high pressure ratios (upto 20:1) are possible without overheating the compressor.
The capacity of the screw compressor is normally controlled with the help of a
slide valve. As the slide valve is opened, some amount of suction refrigerant
escapes to the suction side without being compressed. This yields a smooth capacity
control from 100 percent down to 10 percent of full load. It is observed that the power
input is approximately proportional to refrigeration capacity upto about 30 percent,
however, the efficiency decreases rapidly, there after.
Figure 20.6 shows the compression efficiency of a twin-screw compressor as
a function of pressure ratio and built-in volume ratio. It can be seen that for a given
built-in volume ratio, the efficiency reaches a peak at a particular optimum pressure
ratio. The value of this optimum pressure ratio increases with built-in volume ratio as
shown in the figure. If the design condition corresponds to the optimum pressure
ratio, then the compression efficiency drops as the system operates at off-design
conditions. However, when operated at the optimum pressure ratio, the efficiency is
much higher than other types of compressors.
As the rotor normally rotates at high speeds, screw compressors can handle
fairly large amounts of refrigerant flow rates compared to other positive displacement
type compressors. Screw compressors are available in the capacity range of 70 to
4600 kW. They generally compete with high capacity reciprocating compressors and
low capacity centrifugal compressors. They are available for a wide variety of
refrigerants and applications. Compared to reciprocating compressors, screw
compressors are balanced and hence do not suffer from vibration problems.
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9. Twin-screw compressors are rugged and are shown to be more reliable than
reciprocating compressors; they are shown to run for 30000 – 40000 hours between
major overhauls. They are compact compared to reciprocating compressors in the
high capacity range.
20.4.2. Single-screw compressors:
As the name implies, single screw compressors consist of a single helical
screw and two planet wheels or gate rotors. The helical screw is housed in a
cylindrical casing with suction port at one end and discharge port at the other end as
shown in Fig. 20.7. Suction and compression are obtained as the screw and gate
rotors unmesh and mesh. The high and low pressure regions in the cylinder casing
are separated by the gate rotors.
The single screw is normally driven by an electric motor. The gate rotors are
normally made of plastic materials. Very small power is required to rotate the gate
rotors as the frictional losses between the metallic screw and the plastic gate rotors
is very small. It is also possible to design the compressors with a single gate rotor.
Similar to twin-screw, lubrication, sealing and compressor cooling is achieved by
injecting lubricating oil into the compressor. An oil separator, oil cooler and pump are
required to circulate the lubricating oil. It is also possible to achieve this by injecting
liquid refrigerant, in which case there is no need for an oil separator.
(Pd/Ps)
Vb
ηc
Fig.20.6: Variation of compression efficiency of a twin-screw compressor with
pressure ratio and built-in volume ratio
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10. 20.5. Scroll compressors:
Scroll compressors are orbital motion, positive displacement type
compressors, in which suction and compression is obtained by using two mating,
spiral shaped, scroll members, one fixed and the other orbiting. Figure 20.8 shows
the working principle of scroll compressors. Figures 20.9 and 20.10 show the
constructional details of scroll compressors. As shown in Fig.20.8, the compression
process involves three orbits of the orbiting scroll. In the first orbit, the scrolls ingest
and trap two pockets of suction gas. During the second orbit, the two pockets of gas
are compressed to an intermediate pressure. In the final orbit, the two pockets reach
discharge pressure and are simultaneously opened to the discharge port. This
simultaneous process of suction, intermediate compression, and discharge leads to
the smooth continuous compression process of the scroll compressor. One part that
is not shown in this diagram but is essential to the operation of the scroll is the anti-
rotation coupling. This device maintains a fixed angular relation of 180 degrees
between the fixed and orbiting scrolls. This fixed angular relation, coupled with the
movement of the orbiting scroll, is the basis for the formation of gas compression
pockets.
As shown in Figs.20.9 and 20.10, each scroll member is open at one end and
bound by a base plate at the other end. They are fitted to form pockets of refrigerant
between their respective base plates and various lines of contacts between the scroll
walls. Compressor capacity is normally controlled by variable speed inverter drives.
Suction
Discharge
Gate rotors
Helical
screw
Fig.20.7: Working principle of a single-screw compressor
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11. Fig.20.8: Working principle of a scroll compressor
Fig.20.9: Main parts of a scroll compressor
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12. Fig.20.10: Different views of a scroll compressor
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13. Currently, the scroll compressors are used in small capacity (3 to 50 kW)
refrigeration, air conditioning and heat pump applications. They are normally of
hermetic type. Scroll compressors offer several advantages such as:
1. Large suction and discharge ports reduce pressure losses during suction and
discharge
2. Physical separation of suction and compression reduce heat transfer to
suction gas, leading to high volumetric efficiency
3. Volumetric efficiency is also high due to very low re-expansion losses and
continuous flow over a wide range of operating conditions
4. Flatter capacity versus outdoor temperature curves
5. High compression efficiency, low noise and vibration compared to
reciprocating compressors
6. Compact with minimum number of moving parts
Questions and Answers:
1. Which of the following statements concerning fixed vane, rotary compressors are
true?
a) These compressors are used in small capacity systems (less than 2 kW)
b) They require suction valve, but do not require discharge valve
c) Refrigerant leakage is minimized by hydrodynamic lubrication
d) Compared to reciprocating compressors, the re-expansion losses are high in
rotary vane compressor
Ans.: a) and c)
2. Which of the following statements concerning multiple vane, rotary compressors
are true?
a) Compared to fixed vane compressors, the leakage losses are less in multiple
vane compressors
b) Multiple vane compressors do not require suction and discharge valves
c) A non-return, check valve is used on suction side of the compressor to minimize
cycling losses
d) All of the above
Ans.: d)
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14. 3. Which of the following statements concerning rotary vane type compressors are
not true?
a) They are compact due to high volumetric efficiency
b) They are ideal for transport applications due to low mass-to-capacity ratio
c) They are easier to manufacture compared to reciprocating compressors
d) They are better balanced, and hence, offer lower noise levels
Ans.: c)
4. For a twin-screw type compressors with 5 male lobes and a rotational speed of
3000 RPM, the number of discharges per minute are:
a) 600
b) 15000
c) 1200
d) 3000
Ans.: b)
5. Twin-screw compressors can be operated at high pressure ratios because:
a) These compressors are designed to withstand high discharge temperatures
b) Lubricating oil, which also acts as a coolant is injected between the rotors
c) The cold suction gas cools the rotors during suction stroke
d) All of the above
Ans.: b)
6. Which of the following statements concerning screw compressors are true?
a) Compared to reciprocating compressors, screw compressors are rugged and are
more reliable
b) Screw compressors are easier to manufacture and are cheaper compared to
reciprocating compressors
c) The compression efficiency of a screw compressor increases with built-in volume
ratio
d) Screw compressors are available in refrigeration capacity ranging from fractional
kilowatts to megawatts
Ans.: a)
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15. 7. Which of the following statements concerning screw compressors are true?
a) The capacity of a screw compressor can be varied over a large range by using the
slide valve
b) Compared to reciprocating compressors, screw compressors are compact for
small capacities and bulky for large capacities
c) An oil separator and an oil cooler are required in a screw compressor irrespective
of the type of refrigerant used
d) Vibration is one of the practical problems in operating screw compressors
Ans.: a) and c)
8. Which of the following statements concerning scroll compressors are true:
a) Currently available scroll compressors are of open type
b) Currently scroll compressors are available for large capacities only
c) The possibility of suction gas heating is less in scroll compressors
d) Scroll compressors are easier to manufacture
Ans.: c)
9. The advantages of scroll compressors are:
a) High volumetric efficiency
b) Capacity is less sensitive to outdoor conditions
c) Compactness
d) Low noise and vibration
e) All of the above
Ans.: e)
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